Control apparatus and control method for internal combustion engine

ABSTRACT

A control apparatus stops supply of a fuel to an engine (a) when a value of a parameter relating to a misfire of the engine satisfies a misfire condition that is set based on an octane value of the fuel, or (b) when it is determined that a misfire may occur if an increased amount of the fuel is supplied to the engine in the case where ignition timing of the engine is retarded based on an octane value of the fuel, and the amount of the fuel is increased according to a retard amount of the ignition timing.

INCORPORATION BY REFERENCE

The disclosure of Japanese Patent Application No. 2003-391035 filed onNov. 20, 2003, including the specification, drawings and abstract, areincorporated herein by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of Invention

The invention relates to a control apparatus and control method for aninternal combustion engine, and more particularly to a control apparatusand control method for an internal combustion engine in which an octanevalue of a fuel being used is changed.

2. Description of Related Art

In a typical gasoline engine, knocking is more likely to occur as anoctane value of a fuel becomes lower. When a low-octane fuel is used inthe gasoline engine, ignition timing is usually retarded compared to theignition timing at which optimal performance can be obtained if astandard-octane fuel is used. The ignition timing is retarded by anamount based on the octane value of the low-octane fuel so as to preventoccurrence of knocking.

However, as the ignition timing is retarded, an exhaust gas temperatureincreases in the gasoline engine. Therefore, when the ignition timing isretarded in order to prevent occurrence of knocking as described above,the temperature of components of an exhaust system may excessivelyincrease due to an increase in the exhaust gas temperature duringhigh-load operation or the like, which may lead to a decrease in theeffective lifetime of the components of the exhaust system.

Thus, the temperature of the exhaust system is maintained at or below apredetermined temperature (for example, an upper limit temperature at orbelow which reliability of the components of the exhaust system can bemaintained) by increasing an amount of the fuel injected to the enginesuch that an air-fuel ratio is reduced (i.e., the air-fuel ratio is maderich) in an engine operating region in which the exhaust gas temperatureincreases.

Japanese Patent Laid-Open Publication No. 2001-50081 discloses anexample of an engine in which the exhaust system temperature iscontrolled by increasing the fuel injection amount as described above.

In the engine disclosed in the aforementioned Japanese Patent Laid-OpenPublication No. 2001-50081, since the fuel injection amount is increasedbased on the octane value of a fuel, in an engine operating region inwhich overheating of an exhaust system needs to be prevented, it ispossible to increase the fuel injection amount by an appropriate amounteven when the octane value of the fuel is changed. Thus, it is possibleto prevent a decrease in fuel efficiency due to overheating of theexhaust system or an excessive increase in the fuel injection amount.

Meanwhile, in the engine disclosed in the Japanese Patent Laid-OpenPublication No. 2001-50081, since the amount by which the fuel injectionamount is increased is decided based on the octane value of the fuel,the fuel injection amount needs to be increased by a larger amount asthe degree of the increase in the exhaust system temperature due toretard of the ignition timing becomes larger, when the octane value ofthe fuel becomes lower.

However, in the case where the fuel injection amount is increased by alarger amount in order to suppress the increase in the exhaust systemtemperature as the octane value of the fuel is lower, an air-fuelmixture in a combustion chamber may become excessively rich and amisfire limit may be reached. This is particularly possible in anoperating state where the exhaust gas temperature becomes high and alow-octane fuel is used.

For example, a fuel supply device may supply at least two fuels havinggreatly different octane values, such as a high-octane gasoline havingan extremely high octane value and a low-octane gasoline having anextremely low octane value, in a given proportion, and the proportionmay be changed according to an engine operating condition or the like sothat the octane value of the entire fuel supplied to the engine can bechanged according to the engine operating condition or the like whilethe engine is operated. In this case, the octane value of the fuel beingused varies within a large range.

Accordingly, in the case where the increase in the exhaust systemtemperature is suppressed by increasing the fuel injection amount duringthe high-load operation or the like and when the octane value is lowest,the fuel injection amount needs to be increased by a large amount, whichmay lead to occurrence of a misfire in a combustion chamber due to arich air-fuel ratio.

SUMMARY OF THE INVENTION

In view of the above problems, it is one object of the invention toprovide a control apparatus and control method for an internalcombustion engine, which makes it possible to prevent (or at leastreduces the possibility of) an excessive increase in an exhaust systemtemperature while preventing occurrence of a misfire due to a richair-fuel ratio in an internal combustion engine in which ignition timingis retarded, even when a low-octane fuel is used.

According to a first aspect of the invention, a control apparatus for aninternal combustion engine includes a controller that retards ignitiontiming of the engine, and increases an amount of a fuel supplied to theengine based on a retard amount of the ignition timing. The controllerstops supply of the fuel to the engine when a value of a parameterrelating to a misfire of the engine satisfies a misfire condition setbased on an octane value of the fuel.

In the first aspect of the invention, the supply of the fuel to theengine is stopped when the value of a parameter relating to a misfire ofthe engine, such as an amount of the fuel supplied to the engine, anengine intake air amount, and ignition timing, satisfies the misfirecondition. In the first aspect of the invention, for example, the supplyof the fuel to the engine may be stopped when the value of the parameterhas reached a limit value corresponding to the misfire condition. Thelimit value of the parameter corresponding to the misfire conditionvaries depending on the octane value of the fuel. Accordingly, in thefirst aspect of the invention, the controller may change the limit valueof the parameter based on the octane value of the fuel. In this case,since the limit value of the parameter is changed based on the octanevalue of the fuel, it is possible to prevent an excessive increase in anexhaust system temperature by suppressing an increase in an exhaust gastemperature without causing a misfire even when the octane value of thefuel is changed.

According to a second aspect of the invention, a control apparatus foran internal combustion engine includes a controller that retardsignition timing of the engine, and increases an amount of a fuelsupplied to the engine based on a retard amount of the ignition timing.The controller determines whether a misfire may occur in the engine ifan increased amount of the fuel is supplied to the engine, and stopssupply of the fuel to the engine when it is determined that a misfiremay occur.

In the second aspect of the invention, in the case where an increase inan exhaust system temperature is suppressed by increasing the amount ofthe fuel supplied to the engine, it is determined whether a misfire mayoccur if the engine is supplied with the fuel of the amount required formaintaining the exhaust system temperature at or below an upper limittemperature. When it is determined that a misfire may occur, the supplyof the fuel to the engine is stopped. Thus, in the case where the octanevalue of the fuel is low, and the amount of the fuel supplied to theengine needs to be increased by a large amount in order to suppress theincrease in the exhaust system temperature, fuel cut is performed.Accordingly, it is possible to prevent overheating of the exhaust systemwhile preventing occurrence of a misfire.

According to a third aspect of the invention, a control apparatus for aninternal combustion engine includes a controller that retards ignitiontiming of the engine, and increases an amount of a fuel supplied to theengine based on a retard amount of the ignition timing. The controllercalculates a maximum engine intake air amount at which an exhaust systemtemperature can be maintained at or below a predetermined upper limittemperature by increasing the amount of the fuel supplied to the enginewithout causing a misfire of the engine, and limits an engine intake airamount to a value no greater than the maximum engine intake air amount.

In the third aspect of the invention, the engine intake air amount islimited so as to prevent occurrence of a misfire due to an increase inthe amount of the fuel supplied to the engine. The amount of the fuelsupplied to the engine is increased as the engine intake air amount(engine load) is increased. Also, the degree of an increase in theexhaust system temperature due to retard of the ignition timing becomeslarger as the engine intake air amount becomes larger. In order tosuppress this increase in the exhaust system temperature, the amount ofthe fuel supplied to the engine needs to be further increased. Thus, theamount of the fuel supplied to the engine is increased by a largeramount as the engine intake air amount becomes larger. When the engineintake air amount exceeds a certain amount, the exhaust systemtemperature cannot be maintained at or below the predetermined upperlimit temperature unless the amount of the fuel is increased beyond apoint where a misfire limit is reached.

Accordingly, in the third aspect of the invention, the engine intake airamount is prevented from exceeding the maximum engine intake air amountat which the exhaust system temperature can be maintained at or belowthe predetermined upper limit temperature by increasing the amount ofthe fuel supplied to the engine without causing a misfire of the engine.Thus, it is possible to prevent overheating of the exhaust system whilepreventing occurrence of a misfire.

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing and further objects, features and advantages of theinvention will become apparent from the following description ofpreferred exemplary embodiments with reference to the accompanyingdrawings, wherein like numerals are used to represent like elements andwherein:

FIG. 1 is a schematic diagram showing a configuration of an embodimentof the invention applied to an internal combustion engine for anautomobile;

FIG. 2 is a flow chart explaining an exhaust system temperaturesuppression control operation according to a first exemplary embodimentof the invention;

FIG. 3 is a flow chart explaining an exhaust system temperaturesuppression control operation according to a second exemplary embodimentof the invention;

FIG. 4 is a flow chart explaining an exhaust system temperaturesuppression control operation according to a third exemplary embodimentof the invention;

FIG. 5 is a flow chart explaining an exhaust system temperaturesuppression control operation according to a fourth exemplary embodimentof the invention; and

FIG. 6 is a graph explaining a relationship between an acceleratoropening degree and a throttle valve opening degree.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

Hereinafter, exemplary embodiments of the invention will be describedwith reference to the accompanying drawings. FIG. 1 is a schematicdiagram showing a configuration of an internal combustion engine for avehicle to which embodiments of the invention is applied.

In FIG. 1, fuel injection valves 110H and 110L inject a fuel into eachcylinder of an internal combustion engine for a vehicle 100. In thisembodiment of the invention, one fuel injection valve 110H and one fuelinjection valve 110L are provided for each cylinder. Since afour-cylinder gasoline engine is used in the embodiment shown in FIG. 1,four fuel injection valves 110H and four fuel injection valves 110L areprovided. That is, eight fuel injection valves are provided in total.

The fuel injection valve 110H is referred to also as “high-octanegasoline injection valve”, and supplies a high-octane gasoline to eachcylinder. The fuel injection valve 110L is referred to also as“low-octane gasoline injection valve”, and supplies a low-octanegasoline to each cylinder. Each high-octane gasoline injection valve110H is connected to a high-octane gasoline delivery pipe 20H. Eachlow-octane gasoline injection valve 110L is connected to a low-octanegasoline delivery pipe 20L. Each high-octane gasoline injection valve110H injects the fuel in the high-octane gasoline delivery pipe 20H intoits corresponding cylinder. Each low-octane gasoline injection valve110L injects the fuel in the low-octane gasoline delivery pipe 20L intoits corresponding cylinder.

In the embodiment shown in FIG. 1, a high-octane gasoline injectionvalve 110H and a low-octane gasoline injection valve 110L are separatelyprovided for each cylinder. However, the high-octane gasoline deliverypipe 20H and the low-octane gasoline delivery pipe 20L may be connectedto a single in-cylinder fuel injection valve. In this case, thehigh-octane gasoline and the low-octane gasoline may be mixed in apredetermined proportion before being supplied to the fuel injectionvalve, or the high-octane gasoline and the low-octane gasoline may bemixed in the predetermined proportion in the fuel injection valve afterbeing supplied to the fuel injection valve.

Also, either the high-octane gasoline injection valve or the low-octanegasoline injection valve may be a typical port fuel injection valveprovided in an intake port of each cylinder, or both of the injectionvalves may be typical port fuel injection valves provided in the intakeport of each cylinder.

In FIG. 1, fuel tanks 11H and 11L for the engine 100 are provided. Inthe embodiment, since two fuels having different properties are injectedinto the engine from the fuel injection valves 110H and 110L, two fueltanks for the two fuels are separately provided. Although FIG. 1 showsthe case where the high-octane gasoline and the low-octane gasoline areused, a gasoline and another liquid fuel or the like may be used in theembodiment, instead of using two gasolines.

In FIG. 1, the high-octane gasoline is stored in the fuel tank 11H, andthe low-octane gasoline is stored in the fuel tank 11L. The high-octanegasoline and the low-octane gasoline may be separately supplied to thefuel tanks 11H and 11L respectively, from the outside. Also, forexample, the high-octane gasoline and the low-octane gasoline may begenerated by separating a commercially-available gasoline into agasoline containing a large amount of a high octane component and agasoline containing a large amount of a low octane component usingappropriate means such as a separation membrane.

The fuels stored in the fuel tanks 11H and 11L are pressurized by fuelinjection pumps 21H and 21L, which may include a pumping volume controlmechanism, after being supplied to the corresponding pumps 21H and 21Lthrough pipes 15H and 15L. Thus, the fuel stored in the fuel tank 11H issupplied to the fuel injection valve 110H via a fuel supply pipe 25H,and the fuel stored in the fuel tank 11L is supplied to the fuelinjection valve 110L via a fuel supply pipe 25L. Then, each of the fuelsis injected from each of the fuel injection valves into a combustionchamber of each cylinder of the engine 100.

That is, in the embodiment, the high-octane gasoline and the low-octanegasoline are supplied to each cylinder via supply routes which areindependent of each other. Also, the fuel injection amount of each fuelinjection valve is controlled individually. Therefore, the proportionbetween the high-octane gasoline and the low-octane gasoline supplied tothe engine can be set to any value.

In FIG. 1, an electronic control unit (hereinafter, referred to as“ECU”) 30 for the engine 100 is provided. In the embodiment, the ECU 30is configured as a microcomputer having a known configuration in which aread only memory (ROM), a random access memory (RAM), a centralprocessing unit (CPU), and input/output ports are connected by abi-directional bus. The ECU 30 performs a basic control of the ignitiontiming of each cylinder of the engine, the amount of the fuel injectedinto each cylinder, and the like. Also, in the embodiment, the ECU 30sets the proportion between the high-octane gasoline and the low-octanegasoline that are supplied to the engine based on the engine load, andperforms an ignition timing control for setting a retard amount of theignition timing of the engine based on the proportion between thehigh-octane gasoline and the low-octane gasoline. Further, the ECU 30performs an exhaust system temperature suppression control forincreasing the fuel injection amount based on the retard amount of theignition timing and the engine operating state so as to prevent anexhaust system temperature from exceeding a predetermined upper limittemperature due to an increase in an exhaust gas temperature as a resultof retarding the ignition timing. The exhaust system temperaturesuppression control in the embodiment will be described in detail later.

In order to perform these controls, the output port of the ECU 30 isconnected to the fuel injection valves 110H and 110L for each cylindervia a driving circuit (not shown), and the ECU 30 controls the fuelinjection amount of each fuel injection valve. Also, the output port ofthe ECU 30 is connected to an ignition plug (not shown) for eachcylinder via an ignition circuit (not shown), and the ECU 30 controlsthe ignition timing of the engine. The input port of the ECU 30 receivesa signal indicative of a remaining amount of the high-octane gasoline inthe fuel tank 11H and a signal indicative of a remaining amount of thelow-octane gasoline in the fuel tank 11L from fuel remaining amountsensors 12H and 12L provided in the fuel tanks 11H and 11L,respectively. Also, the input port of the ECU 30 receives a signalindicative of an engine rotational speed of the engine 100 from anengine rotational speed sensor 33, a signal indicative of an intake airamount of the engine (hereinafter, referred to as “engine intake airamount”) from an air flow meter 35 provided in an intake passage of theengine, and a signal indicative of an accelerator opening degree (adepression amount of an accelerator pedal operated by a driver) from anaccelerator opening degree sensor 37 disposed in the vicinity of theaccelerator pedal (not shown).

In the embodiment, the accelerator pedal is not mechanically connectedto the intake passage of the engine, and an electronically controlledthrottle valve (not shown), which is operated by an independentactuator, is provided. The ECU 30 performs a calculation to convert theaccelerator opening degree received from the accelerator opening degreesensor 37 into a throttle valve opening degree based on a predefinedrelationship, and controls the electronically controlled throttle valveso that the throttle valve opening degree becomes equal to thecalculated throttle valve opening degree (i.e., a target throttle valveopening degree) by driving the actuator for the throttle valve.

In the embodiment, the ECU 30 sets a total amount of the high-octanegasoline and the low-octane gasoline that are supplied to the engine,and the proportion between the high-octane gasoline and the low-octanegasoline, based on an engine load condition (for example, the engineintake air amount per one revolution of the engine, and the enginerotational speed) according to a predefined relationship. For example,the ECU 30 increases the proportion of the high-octane gasoline when theengine load is high while the engine is operated, as compared to whenthe engine load is low. As a result, the octane value of the entire fuelsupplied to the engine is increased. Accordingly, the engine can beoperated with the ignition timing being sufficiently advanced near tothe ignition timing at which the maximum engine output can be obtained,and the engine output can be increased.

Meanwhile, the proportion of the low-octane gasoline is increased, forexample, when the temperature of the engine is low or when the enginerotational speed is high and the engine load is low while the engine isoperated. As a result, the octane value of the entire fuel is decreasedand ignitionability of the fuel is improved. Accordingly, combustion isstabilized, and properties of engine exhaust gas are improved.

Further, in the case where two fuels such as the high-octane gasolineand the low-octane gasoline are supplied from separate fuel tanks as inthis embodiment, it may be necessary to increase the proportion of thefuel whose remaining amount is larger in order to balance the remainingamounts of the two fuels, irrespective of the engine operating state.Therefore, the fuel having a low octane value may be supplied to theengine even during the high-load engine operation.

Meanwhile, since knocking is more likely to occur when the octane valueof the fuel becomes lower, it is desirable to prevent occurrence ofknocking by retarding the ignition timing of the engine based on adecrease in the octane value. However, since the timing at which theair-fuel mixture is burned in the cylinder is retarded if the ignitiontiming of the engine is retarded, burned gas is discharged from anexhaust valve to the outside of the cylinder before the temperature ofthe burned gas decreases. Therefore, the exhaust gas temperatureincreases as the retard amount of the ignition timing increases.

Meanwhile, durability (useful life) of components of the exhaust systemdecreases if the exhaust gas temperature excessively increases.Therefore, in order to protect the components of the exhaust system, itis desirable to maintain the exhaust system temperature at or below anupper limit temperature at or below which durability of the componentsdoes not decrease, by suppressing the increase in the exhaust gastemperature. Accordingly, in this embodiment, the increase in theexhaust gas temperature is suppressed by increasing the amount of thefuel supplied to the engine based on the engine operating state and theretard amount of the ignition timing so that the combustion air-fuelratio in the engine decreases (i.e., the air-fuel ratio becomes rich).The fuel supply amount is increased by a larger amount as the retardamount of the ignition timing becomes larger, that is, the octane valueof the fuel becomes lower, if other conditions remain the same.

In most cases, the exhaust system temperature can be effectivelymaintained at or below the upper limit temperature by increasing thefuel supply amount based on the retard amount of the ignition timing asdescribed above. However, a problem may occur depending on the engineoperating state and the octane value of the fuel. For example, in thecase where the proportion of the low-octane gasoline is increased inorder to adjust the balance between the remaining amounts of thehigh-octane gasoline and the low-octane gasoline, and therefore theoctane value of the entire fuel is decreased during the high-load engineoperation, a misfire may occur if the fuel supply amount is increased inorder to decrease the exhaust gas temperature.

During the high-load engine operation, the air-fuel ratio is set to aslightly low value (that is, the fuel supply amount is increased), andaccordingly the exhaust gas temperature is high in general. Therefore,if the octane value is decreased to a large extent during the high-loadengine operation, the ignition timing is retarded by a large amount inorder to prevent occurrence of knocking, and the exhaust gas temperaturebecomes even higher. Thus, in order to suppress such a large increase inthe exhaust gas temperature by increasing the fuel supply amount, thefuel supply amount needs to be increased by a large amount. However,since the air-fuel ratio is set to a low value during the high-loadengine operation, the air-fuel ratio excessively decreases (that is, theair-fuel ratio becomes excessively rich), and a misfire may occur due toa rich air-fuel ratio if the fuel supply amount is increased by a largeamount.

Accordingly, in the embodiment, the increase in the exhaust systemtemperature is suppressed while preventing occurrence of a misfire dueto a rich air-fuel ratio using the method described below.

In a first embodiment, it is determined whether a misfire may occur inthe engine if the fuel supply amount is increased in order to suppressthe increase in the exhaust system temperature. When it is determinedthat a misfire may occur, fuel cut is performed so that the exhaustsystem temperature is decreased without increasing the fuel supplyamount.

In other words, every time the engine is operated in an engine operatingregion in which a misfire may occur if the fuel supply amount isincreased in order to suppress the increase in the exhaust systemtemperature, the fuel cut is performed. As a result, the engine isprevented from being operated in the aforementioned region. Therefore,it becomes possible to maintain the exhaust system temperature at orbelow the upper limit temperature without causing a misfire in theengine due to a rich air-fuel ratio.

FIG. 2 is a flow chart explaining the operation of the aforementionedcontrol for suppressing the increase in the exhaust system temperature(referred to as “exhaust system temperature suppression control”). Thecontrol operation is performed as a routine. The routine is performed bythe ECU 30 at predetermined time intervals.

After the control operation shown in FIG. 2 is started, in step S201,the ECU 30 reads a proportion FR between the high-octane fuel and thelow-octane fuel in a present fuel (or the proportion of the low-octanefuel in the entire fuel). The proportion FR is set by an operation (notshown) performed by the ECU 30 separately, based on the engine load (theengine intake air amount per one revolution of the engine) and theengine rotational speed according to a predefined relationship.Alternatively, the proportion FR is set to a value required foradjusting the balance between the remaining amounts of the high-octanefuel and the low-octane fuel.

Next, in step S203, a basic retard amount RFR is calculated based on theproportion FR obtained in step S202, the engine rotational speed, andthe engine load. The basic retard amount RFR is the retard amountoptimal for preventing occurrence of knocking, which is decided based ona difference between a standard octane value of the fuel (a standardproportion) and a present octane value of the fuel (present proportionFR). The values of the basic retard amount RFR have been alreadyobtained in advance through experiments using an actual engine. In theembodiment, the values of the basic retard amount RFR have been storedin the form of a three-dimensional numerical map using the enginerotational speed, the engine load, and the proportion FR as parameters.The basic retard amount RFR increases as the octane value of the fueldecreases if the engine rotational speed and the engine load remain thesame.

After the basic retard amount RFR is calculated in step S203, a knockinglearning value RGKN is read in step S205. The knocking learning valueRGKN is a correction amount by which the basic retard amount RFR iscorrected for preventing occurrence of knocking. The basic retard amountis decided according to a change in the octane value of the fuel whenthe engine is operated in a standard engine operating state. Therefore,the basic retard amount is the retard amount optimal for preventingoccurrence of knocking and maintaining engine performance when theengine is operated in the standard engine operating state. However, forexample, when the engine operating state such as the atmosphericpressure, atmospheric temperature, and humidity changes from thestandard engine operating state to a different engine operating state,the optimal retard amount changes according to the change in the engineoperating state.

Accordingly, the ECU 30 monitors occurrence of knocking using a knockingsensor (not shown) or the like while the engine is actually operated.The ECU 30 detects the ignition timing at which knocking actually occursin the vicinity of the retarded ignition timing based on the basicretard amount RFR. Then, the ECU 30 stores a difference between thedetected ignition timing and the retarded ignition timing based on thebasic retard amount RFR, as the knocking learning value RGKN.

In step S207, a final retard amount RFIN is calculated. The final retardamount RFIN is calculated by correcting the basic retard amount RFRusing the knocking learning value RGKN. That is, the final retard amountRFIN is calculated according to an equation RFIN=RFR+RGKN. The finalretard amount RFIN calculated in step S207 is used as the actual retardamount of the ignition timing of the engine.

Next, in step S209, a fuel increase amount EFOTP is calculated based onthe final retard amount RFIN calculated in step S207. The fuel increaseamount EFOTP is the minimum amount of fuel increase, which is requiredfor maintaining the exhaust system temperature at or below the upperlimit temperature that is the maximum allowable temperature ofcomponents of the exhaust system. The values of the fuel increase amountEFOTP have been already obtained in advance through experiments or thelike, and have been stored in the ROM of the ECU 30 in the form of athree-dimensional numerical map using the final retard amount RFIN, theengine rotational speed, and the engine load as parameters. In stepS209, the fuel increase amount EFOTP is calculated based on the finalretard amount RFIN calculated in step S207, the present enginerotational speed, and the present engine load, according to thenumerical map.

In step S211 and step S213, it is determined whether a misfire willoccur due to a rich air-fuel ratio if the fuel supply amount isincreased by the fuel increase amount EFOTP.

That is, in step S211, a fuel supply amount above which a misfire occursdue to a rich air-fuel ratio is calculated based on a relationship thatis obtained in advance through experiments, and a maximum fuel increaselimit amount EFmax, which is the fuel increase amount corresponding tothe fuel supply amount above which a misfire occurs is calculated. Then,in step S213, it is determined whether the fuel increase amount EFOTPcalculated in step S209 exceeds the maximum fuel increase limit amountEFmax.

In step S213, when the fuel increase amount EFOTP is equal to or lessthan the maximum fuel increase limit amount EFmax, there is nopossibility that a misfire will occur even if the fuel supply amount isincreased by the fuel increase amount EFOTP. Therefore, step S215 andsubsequent steps are not performed, and the value of a fuel cutannouncement flag EXF is set to 0 in step S223 as described later. Then,the present routine is terminated.

Meanwhile, when the fuel increase amount EFOTP is greater than themaximum fuel increase limit amount EFmax, a misfire may occur if thefuel supply amount is increased by the fuel increase amount EFOTP.Therefore, in step S215, the fuel increase amount EFOTP is limited tothe maximum fuel increase limit amount EFmax, and the value of the fuelcut announcement flag EXF is set to 1. Then, the routine proceeds tostep S217.

The fuel cut announcement flag EXF indicates whether there is a largepossibility that the fuel cut will be performed in a present engineoperating state. When the fuel cut announcement flag is set to 1, amisfire should not occur since the fuel increase amount EFOTP is limitedto the maximum fuel increase limit amount EFmax in step S215, but thereis a large possibility that the fuel cut will be performed due tooverheating of the exhaust system. Accordingly, in the embodiment, whenthe fuel cut announcement flag EXF is set to 1, a warning lamp providedfor the driver is turned on to notify the driver that there is a largepossibility that the fuel cut will be performed.

After the fuel cut announcement flag EXF is set to 1 in step S215, apresent exhaust system component representative temperature TMP iscalculated in step S217. The exhaust system component representativetemperature TMP represents the temperature of the components of theexhaust system. The exhaust system component representative temperatureTMP is calculated based on the present exhaust system temperature. Thetemperature of the components of the exhaust system increases accordingto the increase in the exhaust system temperature. Thus, it isconsidered that an exhaust system component representative temperatureincrease value ΔTMP, which is an increase in the exhaust systemcomponent representative temperature TMP per unit time, is proportionalto a difference between an exhaust system temperature EXT and theexhaust system component representative temperature TMP.

Accordingly, the present exhaust system component representativetemperature TMP is obtained by an equation TMP=ΔTMP+TMP_(i-1,) in whichTMP_(i-1) is an exhaust system component representative temperature aunit time ago. The exhaust system component representative temperatureincrease value ΔTMP is obtained by an equation ΔTMP=K×(EXT−TMP_(i-1)),in which K is a constant value.

The values of the exhaust system temperature EXT have been stored inadvance in the ROM of the ECU 30 in the form of a numerical map usingthe engine rotational speed, engine load, the retard amount of theignition timing, and the air-fuel ratio of the engine (i.e., the fuelincrease amount), as parameters.

The ECU 30 starts to calculate the exhaust system temperature EXT andthe exhaust system component representative temperature increase valueΔTMP using an appropriate initial value of the exhaust system componentrepresentative temperature TMP (for example, the atmospherictemperature) when the engine is started. Thus, the ECU 30 calculates thepresent exhaust system component representative temperature TMP byaccumulating the values of ΔTMP.

In step S219, it is determined whether the present exhaust systemcomponent representative temperature TMP calculated in step S217 exceedsa predetermined maximum allowable temperature TMPmax. When the presentexhaust system component representative temperature TMP is higher thanthe predetermined maximum allowable temperature TMPmax (TMP>TMPmax), thefuel cut is performed in step S221.

That is, in the embodiment, it is determined whether the actual exhaustsystem component representative temperature TMP exceeds the maximumallowable temperature TMPmax due to the increase in the exhaust systemtemperature. That is, it is determined whether overheating of theexhaust system actually occurs, instead of simply determining whetherthe exhaust system temperature exceeds the upper limit temperature. Thefuel cut is performed only when the overheating actually occurs. Thus,in this embodiment, the frequency with which the fuel cut is performedis reduced while reliably preventing actual overheating of the exhaustsystem.

In the embodiment, it is determined whether the fuel cut needs to beperformed based on whether the exhaust system component representativetemperature TMP exceeds the maximum allowable temperature (step S219,and step S221), as described above. However, the fuel cut may beperformed immediately when the exhaust system temperature EXT, which iscalculated based on the engine rotational speed, the retard amount, theair-fuel ratio, and the like, exceeds a predetermined upper limittemperature. Owing to the control operation described above, theincrease in the exhaust system temperature of the engine can besuppressed while preventing occurrence of a misfire even when theignition timing is retarded due to use of a low-octane fuel. Also, inthis embodiment, the calculated fuel increase amount EFOTP is comparedwith the maximum fuel increase limit amount EFmax, and the fuel increaseamount EFOTP is limited to the maximum fuel increase limit amount EFmaxwhen the fuel increase amount EFOTP is greater than the maximum fuelincrease limit amount EFmax (EFOTP>EFmax). However, supply of the fuelto the engine may be stopped, that is, the fuel cut may be performedwhen the fuel increase amount EFOTP is greater than the maximum fuelincrease limit amount EFmax (EFOTP>EFmax).

Next, the operation of the exhaust system temperature suppressioncontrol according to a second embodiment will be described withreference to FIG. 3. In the second embodiment, a maximum engine intakeair amount GAmax (gram per second) is calculated in advance. The maximumengine intake air amount GAmax is the upper limit value of the engineintake air amount, at or below which the exhaust system componentrepresentative temperature TMP can be maintained at or below the maximumallowable temperature TMPmax without causing a misfire. When an actualengine intake air amount GA exceeds the maximum engine intake air amountGAmax, the fuel cut is performed.

The exhaust system temperature of the engine becomes higher as theengine load becomes higher, that is, as the engine intake air amountbecomes larger. Therefore, in order to maintain the exhaust systemtemperature at or below the upper limit temperature when the engine isoperated with the ignition timing being retarded, it is desirable todecrease the exhaust system temperature by decreasing the air-fuel ratioto a larger extent as the retard amount of the ignition timing becomeslarger, and as the engine intake air amount becomes larger.

Accordingly, when the retard amount of the ignition timing is decided,the air-fuel ratio required for maintaining the exhaust systemtemperature at or below the upper limit temperature becomes a functionof the engine intake air amount. Therefore, when the retard amount ofthe ignition timing is decided, the maximum engine intake air amountGAmax above which the air-fuel ratio becomes equal to or less than arich misfire limit is decided. In this embodiment, the maximum intakeamount GAmax is obtained based on the retard amount of the ignitiontiming, and the fuel cut is performed when the actual engine intake airamount exceeds the maximum engine intake air amount. Thus, the exhaustsystem temperature can be maintained at or below the upper limittemperature without causing a misfire.

FIG. 3 is a flow chart specifically explaining the operation of thisexhaust system temperature suppression control. The control operation isperformed as a routine. The routine is performed by the ECU 30 atpredetermined time intervals.

After the control operation shown in FIG. 3 is started, the proportionFR is read in step S301, and the knocking learning value RGKN is read instep S303. The proportion FR and the knocking learning value RGKN arethe same as those used in the control according to the first embodimentshown in FIG. 2. In the second embodiment, the maximum engine intake airamount GAmax is directly calculated using the proportion FR and theknocking learning value RGKN in step S305.

As described above, the maximum engine intake air amount GAmax is theupper limit value of the engine intake air amount, at or below which theexhaust system component representative temperature TMP can bemaintained at or below the maximum allowable temperature TMPmax withoutcausing a misfire due to a rich air-fuel ratio. The maximum engineintake air amount GAmax is a function of the retard amount of theignition timing of the engine. That is, since the retard amount of theignition timing is set based on the octane value, the maximum engineintake air amount GAmax (the upper limit value of the engine intake airamount above which a misfire occurs) also is changed based on the octanevalue.

As described above with reference to FIG. 2, the final retard amountRFIN is the sum of the basic retard amount RFR and the knocking learningvalue RGKN. Also, the basic retard amount RFR is decided based on theoctane value of the fuel (that is, the proportion FR), and the knockinglearning value RGKN is decided according to the actual engine operatingstate. Thus, in this embodiment, the values of the final retard amountRFIN have been calculated based on the values of the proportion FR andthe values of the knocking learning value RGKN in advance. Further, thevalue of the maximum engine intake air amount GAmax corresponding toeach value of the final retard amount RFIN has been calculated inadvance, and has been stored in the ROM of the ECU 30 in the form of atwo-dimensional numerical map using the proportion FR and knockinglearning value RGKN as parameters. In step S305, the present maximumengine intake air amount GAmax is obtained based on the presentproportion FR and the present knocking learning value RGKN, according tothe numerical map.

Next, in step S307, the present engine intake air amount GA is read fromthe air flow meter 35. In step S309, it is determined whether the actualengine intake air amount GA exceeds the maximum engine intake air amountGAmax.

When the actual engine intake air amount GA is greater than the maximumintake air amount (GA>GAmax) in step S309, there is a possibility that amisfire may occur due to a rich air-fuel ratio. Therefore, the fuel cutis performed in step S311. Thus, in this embodiment, when the ignitiontiming is retarded based on the octane value of the fuel, it is possibleto prevent occurrence of a misfire due to a rich air-fuel ratio whilemaintaining the exhaust system temperature at or below the upper limittemperature by increasing the fuel supply amount.

Next, the operation of the exhaust system temperature suppressioncontrol according to a third embodiment will be described. In the thirdembodiment, misfire limit ignition timing EAMIS corresponding to thepresent fuel increase amount EFOTP is obtained. The misfire limitignition timing EAMIS is the ignition timing after which a misfirelikely occurs. When present ignition timing EAOP is later than themisfire limit ignition timing EAMIS, the fuel cut is performed.

That is, in this embodiment as well, when the fuel supply amount isincreased such that the air-fuel ratio becomes richer than the air-fuelratio at which the air-fuel mixture can be ignited at the ignitiontiming decided based on the present retard amount RFIN, the fuel cut isperformed. FIG. 4 is a flow chart explaining the operation of theexhaust system temperature suppression control according to the thirdembodiment. The control operation is performed by the ECU 30 atpredetermined time intervals.

In the control operation shown in FIG. 4, first, the fuel increaseamount EFOTP is calculated in step S401. The fuel increase amount EFOTPis calculated by the operation (not shown) performed by the ECU 30separately in the same manner as in the first embodiment that has beendescribed with reference to FIG. 2.

Then, in step S403, the misfire limit ignition timing EAMIScorresponding to the present fuel increase amount EFOTP is calculated.The values of the misfire limit ignition timing EAMIS have been alreadyobtained in advance through experiments or the like, and have beenstored in the ROM of the ECU 30 in the form of a three-dimensionalnumerical map using the engine rotational speed, the engine load, andthe fuel increase amount EFOTP, as parameters.

After the misfire limit ignition timing EAMIS is calculated in stepS403, the actual ignition timing EAOP of the engine is calculated instep S405. The actual ignition timing EAOP is the ignition timing thatis retarded with respect to the ignition timing that is optimal when thefuel having the standard octane value is used, by the final retardamount RFIN. The final retard amount RFIN is separately calculated inthe same manner as in the control according to the first embodimentshown in FIG. 2.

Then, in step S407, the actual ignition timing EAOP is compared with themisfire limit ignition timing EAMIS. When the actual ignition timingEAOP is later than the misfire limit ignition timing EAMIS (EAOP<EAMIS),the fuel cut is performed in step S409.

Next, the operation of the exhaust system temperature suppressioncontrol according to a fourth embodiment of the invention will bedescribed. In the aforementioned second embodiment (FIG. 3), the maximumengine intake air amount GAmax (gram per second) is calculated inadvance. The maximum engine intake air amount GAmax is the upper limitvalue of the engine intake air amount, at or below which the exhaustsystem component representative temperature TMP can be maintained at orbelow the maximum allowable temperature TMPmax without causing a misfirewhen the engine is operated with the ignition timing being retarded bythe present retard amount. When the actual engine intake air amount GAexceeds the maximum engine intake air amount GAmax, the fuel cut isperformed so as to prevent occurrence of a misfire.

In the fourth embodiment as well, the operation of the exhaust systemtemperature suppression control is performed based on the calculatedmaximum engine intake air amount GAmax. However, in the fourthembodiment, the actual engine intake air amount GA is limited to themaximum engine intake air amount GAmax or less without performing thefuel cut, unlike the aforementioned second embodiment in which theactual intake air amount GA is limited to the maximum engine intake airamount GAmax or less by performing the fuel cut when the actual engineintake air amount GA exceeds the maximum engine intake air amount GAmax.

For example, the engine 100 in this embodiment (shown in FIG. 1)includes the electronically controlled throttle valve whose openingdegree can be set independently of the operation of accelerator pedalperformed by the driver. Since the electronically controlled throttlevalve is used in this embodiment, the opening degree of the throttlevalve can be set freely. The electronically controlled throttle valve isusually controlled such that a throttle valve opening degree THA isproportional to an accelerator opening degree ACCP. However, in thisembodiment, after the maximum engine intake air amount GAmax iscalculated, a calculation is performed to obtain the throttle valveopening degree at which the engine intake air amount becomes equal tothe maximum engine intake air amount GAmax in the present engineoperating state (i.e., the present intake air temperature and thepresent engine rotational speed). Then, the relationship between theaccelerator opening degree ACCP and the throttle valve opening degreeTHA is corrected such that the throttle valve opening degree when theaccelerator opening degree is 100% becomes equal to the throttle valveopening degree at which the engine intake air amount becomes equal tothe maximum engine intake air amount.

Thus, the actual engine intake air amount GA is limited to the maximumengine intake air amount GAmax or less, and occurrence of a misfire dueto a rich air-fuel ratio is prevented without performing the fuel cut.

FIG. 5 is a flow chart specifically explaining the operation of theexhaust system temperature suppression control according to theaforementioned fourth embodiment. The control operation is performed bythe ECU 30 at predetermined time intervals.

In the control operation shown in FIG. 5, first, the proportion FR isread in step S501, and the knocking learning value RGKN is read in stepS503. In step S505, the maximum engine intake air amount GAmax iscalculated based on the proportion FR and the knocking learning valueRGKN.

As described above, the maximum engine intake air amount GAmax is theupper limit value of the engine intake air amount, at or below which theexhaust system component representative temperature TMP can bemaintained at or below the maximum allowable temperature TMPmax withoutcausing a misfire due to a rich air-fuel ratio. The operation forcalculating the maximum engine intake air amount GAmax in step S501 tostep S505 in FIG. 5 is the same as the operation in step S301 to stepS305 in FIG.3.

Thus, after the maximum engine intake air amount GAmax is calculated,the throttle valve opening degree THα at which the engine intake airamount becomes equal to the maximum engine intake air amount GAmax iscalculated, based on the present engine operating state in step S507.The engine intake air amount is decided based on the engine rotationalspeed and the throttle valve opening degree when the conditions such asthe atmospheric temperature and the atmospheric pressure remain thesame. In the embodiment, the relationship between the engine intake airamount and the throttle valve opening at each engine rotational speed isobtained when the atmospheric temperature, the atmospheric pressure, andthe like are in the standard state. The values of the throttle valveopening degree have been stored in the ROM of the ECU 30 in the form ofa two-dimensional numerical map using the engine rotational speed andthe engine intake air amount as parameters.

In step S507, the throttle valve opening degree THα at which the engineintake air amount becomes equal to the maximum engine intake air amountGAmax at the present engine rotational speed is calculated by correctingthe numerical map using the present intake air temperature and thepresent atmospheric pressure. After the throttle valve opening degreeTHα is calculated in step S507, a present accelerator opening degree Aβis read from the accelerator opening degree sensor 37, and a presentthrottle valve opening degree THβ is read from a throttle valve openingdegree sensor (not shown) disposed in the vicinity of the throttle valveof the engine in step S509.

In step S511, a throttle valve opening degree correction coefficient K1is calculated according to an equation, K1=(WOT−THβ)/(THα−THβ), in whichWOT is the throttle valve opening degree when the throttle valve isfully open (i.e., opening degree of 100%).

Then, in step S513, the throttle valve opening degree is corrected tothe target throttle valve opening degree that is set using the throttlevalve opening degree correction coefficient K1 .

FIG. 6 is a graph explaining the correction of the throttle valveopening degree using the throttle valve opening degree correctioncoefficient K1, which is performed in step S513. In FIG. 6, a horizontalaxis indicates the accelerator opening degree ACCP, and a vertical axisindicates the throttle valve opening degree THA. Also, on the verticalaxis, WOT indicates the throttle valve opening degree when the throttlevalve is fully open, THα indicates the throttle valve opening degreecorresponding to the maximum engine intake air amount GAmax, and THβindicates the present throttle valve opening degree. On the horizontalaxis, AF indicates the accelerator opening degree when the acceleratorpedal is fully depressed, and Aβ indicates the present acceleratoropening degree corresponding to the throttle valve opening degree THβ.

The ECU 30 usually sets the relationship between the throttle valveopening degree THA and the accelerator opening degree ACCP such that thethrottle valve opening degree THA is proportional to the acceleratoropening degree ACCP, as shown by a solid line in FIG. 6. That is, thethrottle valve opening degree THA is usually calculated according to anequation THA=ACCP×(WOT/AF).

Meanwhile, in this embodiment, when the correction of the throttle valveopening degree is performed using the throttle valve opening degreecorrection coefficient K1, the throttle valve opening degree THA is setusing the present throttle valve opening degree THβ, the presentaccelerator opening degree Aβ, and the throttle valve opening degreecorrection coefficient K1, according to an equation,THA=THβ+(ACCP−Aβ)×(WOT/AF)×K1.

Thus, after the throttle valve opening degree correction coefficient K1is calculated, the throttle valve opening degree is corrected to thetarget throttle valve opening degree that is set based on therelationship between the accelerator opening degree ACCP and thethrottle valve opening degree THA shown by a dashed line. Thus, thethrottle valve opening degree corresponding to the accelerator openingdegree AF (i.e., the accelerator opening degree when the acceleratorpedal is fully depressed) is changed to the throttle valve openingdegree THα. Accordingly, since the maximum throttle valve opening degreeis limited to the throttle valve opening degree THα, the engine intakeair amount GA is maintained at or below the maximum engine intake airamount GAmax.

In this embodiment, the maximum engine intake air amount is limitedusing the electronically controlled throttle valve. However, the sameoperation as in this embodiment can be performed in a typical throttlevalve that is connected to the accelerator pedal using a mechanical linkmechanism, by providing a movable stopper for limiting the maximumthrottle valve opening degree, and moving the position of the stopperaccording to the maximum engine intake air amount GAmax.

In the aforementioned embodiments, when the retard amount of theignition timing is set, the octane value of the entire fuel iscalculated based on the proportion between the two fuels. Thus, even inthe case where the octane value of the entire fuel is changed withrelatively high frequency, the exhaust system temperature suppressioncontrol can be performed easily and promptly. However, another methodfor detecting the octane value of the fuel during the engine operationmay be employed. For example, the ignition timing at which knockingoccurs may be determined while the ignition timing is gradually advancedduring the engine operation, and the octane value of the fuel may beestimated based on the ignition timing at which knocking occurs and theengine operating state according to a predefined relationship.

The controller (e.g., the ECU 30) of the illustrated exemplaryembodiments is implemented as a programmed general purpose computer. Itwill be appreciated by those skilled in the art that the controller canbe implemented using one or more special purpose integrated circuits(e.g., ASIC) having a main or central processor section for overall,system-level control, and separate sections dedicated to performingvarious different specific computations, functions and other processesunder control of the central processor section. The controller can be aplurality of separate dedicated or programmable integrated or otherelectronic circuits or devices (e.g., hardwired electronic or logiccircuits such as discrete element circuits, or programmable logicdevices such as PLDs, PLAs, PALs or the like). The controller can beimplemented using one or more suitably programmed general purposecomputers, e.g., microprocessor, microcontroller or other processordevices (CPU or MPU), either alone or in conjunction with one or moreperipheral (e.g., integrated circuit) data and signal processingdevices. In general, any device or assembly of devices on which a finitestate machine capable of implementing the procedures described hereincan be used as the controller. A distributed processing architecture canbe used for maximum data/signal processing capability and speed.

While the invention has been described with reference to exemplaryembodiments thereof, it is to be understood that the invention is notlimited to the exemplary embodiments and constructions. The invention isintended to cover various modifications and equivalent arrangements. Inaddition, while the various elements of the exemplary embodiments areshown in various combinations and configurations, which are exemplary,other combinations and configuration, including more, less or only asingle element, are also within the spirit and scope of the invention.

1. A control apparatus for an internal combustion engine, comprising: acontroller that retards ignition timing of the engine, and increases anamount of a fuel supplied to the engine based on a retard amount of theignition timing, wherein the controller stops supply of the fuel to theengine when a value of a parameter relating to a misfire of the enginesatisfies a misfire condition which is set based on an octane value ofthe fuel.
 2. The control apparatus according to claim 1, wherein thecontroller stops the supply of the fuel to the engine when the value ofthe parameter has reached a limit value corresponding to the misfirecondition, and changes the limit value based on the octane value of thefuel.
 3. The control apparatus according to claim 1, wherein theparameter is the amount of the fuel supplied to the engine.
 4. Thecontrol apparatus according to claim 1, wherein the parameter is anengine intake air amount.
 5. The control apparatus according to claim 1,wherein the parameter is the ignition timing.
 6. The control apparatusaccording to claim 1, wherein the controller retards the ignition timingof the engine based on an octane value of the fuel.
 7. The controlapparatus according to claim 1, wherein the control apparatus can supplyat least two fuels having different octane values to the internalcombustion engine in a given proportion, and can change the proportionwhile the engine is operated; and the controller retards the ignitiontiming of the engine based on the proportion.
 8. A control apparatus foran internal combustion engine, comprising: a controller that retardsignition timing of the engine, and increases an amount of a fuelsupplied to the engine based on a retard amount of the ignition timing,wherein the controller determines whether a misfire condition issatisfied if an increased amount of the fuel is supplied to the engine,and stops supply of the fuel to the engine when it is determined thatthe misfire condition is satisfied.
 9. The control apparatus accordingto claim 8, wherein the controller retards the ignition timing of theengine based on an octane value of the fuel.
 10. The control apparatusaccording to claim 8, wherein the control apparatus can supply at leasttwo fuels having different octane values to the internal combustionengine in a given proportion, and can change the proportion while theengine is operated; and the controller retards the ignition timing ofthe engine based on the proportion.
 11. A control method for an internalcombustion engine, comprising the steps of: retarding ignition timing ofthe engine; increasing an amount of a fuel supplied to the engine basedon a retard amount of the ignition timing; and stopping supply of thefuel to the engine when a value of a parameter relating to a misfire ofthe engine satisfies a misfire condition which is set based on an octanevalue of the fuel.
 12. The control method according to claim 11, whereinthe supply of the fuel to the engine is stopped when the value of theparameter has reached a limit value corresponding to the misfirecondition, and the limit value is changed based on the octane value ofthe fuel.
 13. A control method for an internal combustion engine,comprising the steps of: retarding ignition timing of the engine;increasing an amount of a fuel supplied to the engine based on a retardamount of the ignition timing; and determining whether a misfirecondition is satisfied if an increased amount of the fuel is supplied tothe engine, and stopping supply of the fuel to the engine when it isdetermined that the misfire condition is satisfied.